EP0196172A2 - Improved rotary valve - Google Patents
Improved rotary valve Download PDFInfo
- Publication number
- EP0196172A2 EP0196172A2 EP86301549A EP86301549A EP0196172A2 EP 0196172 A2 EP0196172 A2 EP 0196172A2 EP 86301549 A EP86301549 A EP 86301549A EP 86301549 A EP86301549 A EP 86301549A EP 0196172 A2 EP0196172 A2 EP 0196172A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- core
- contour
- valve core
- periphery
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/08—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by type of steering valve used
- B62D5/083—Rotary valves
- B62D5/0837—Rotary valves characterised by the shape of the control edges, e.g. to reduce noise
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86638—Rotary valve
- Y10T137/86646—Plug type
- Y10T137/86654—For plural lines
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86638—Rotary valve
- Y10T137/86646—Plug type
- Y10T137/86662—Axial and radial flow
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86718—Dividing into parallel flow paths with recombining
- Y10T137/86743—Rotary
- Y10T137/86751—Plug
Definitions
- This invention relates to the cores of rotary valves of power steering gears, principally of the type wherein the valve core is also the input shaft to the steering gear.
- valve core typically has, in its outer periphery, a plurality of blind ended, longitudinally extending slots separated by lands.
- Journalled on the valve core is a sleeve member having in its bore a similar array of longitudinally extending blind ended slots matching those of the valve core, but in underlap relationship thereto, the slots of the one being wider than the lands of the other so defining a set of longitudinally extending orifices which open and close when relative rotation occurs between the valve core and the sleeve.
- Drilled passages in the valve core and sleeve together with circumferential grooves in the periphery of the sleeve, serve to communicate oil between the slots in the valve core and sleeve, an engine driven oil pump, and right-hand and left-hand hydraulic assist cylinder/chambers incorporated in the steering gear.
- the edges of the valve core slots are substantially radial to the valve axis, but contoured along their length so that, upon relative rotation of the valve elements, shut-off occurs progressively along the valve.
- This progressive phase of shut-off is such that the rate of area change is exponential, so that the rise in oil pressure is directly proportional to valve rotation as the driver applies torque to the steering wheel, so causing the valve to simulate this aspect of the action of the hydraulic reaction valve.
- a short pocket of limited radial depth remains open to the flow of oil but closes rapidly on further rotation of the valve elements as in hydraulic reaction valves.
- Further important aspects of the hydraulic reaction valve, relating to the performance of the valve in the neutral or on-centre driving region are imperfectly simulated in valves made according to that patent, as will be discussed later.
- Valves conforming to U.S. patent 3,591,136 have been widely applied to integral steering gears for several years, but are proving unsatisfactory for use in the more recently preferred rack and pinion type power steering gears, due to the fact that valve metering of the type described in that patent tends to produce hissing noises when operating at other than low pressures.
- Rack and pinion steering gears are now often mounted directly to the engine compartment bulk-head, and such noises are therefore far more apparent to the driver as they are transmitted directly to the car interior.
- Examples of use of the 'sheet flow' hiss-suppressing technique are to be found in several Japanese manufactured steering gears, where the slot edges are each ground over their full length along the valve axis by causing a large cylindrical grinding wheel having its axis of rotation parallel to the valve core to grind one or more short flats on the slot edges almost tangential to the valve periphery.
- valve slot edges having an exponential rate of area cut-off and other geometric features which will be referred to later needed to simulate the hydraulic reaction type valves various specific proportions of the valve edges are required.
- the cross-section of the slot edges of constant cross-secion which are able to provide the exponential rate of area change has a scroll-like contour extending about .6mm around the valve periphery, terminating, at the high pressure end thereof, in a surface nearly concentric with the valve axis.
- valve core edges made according to the invention provide further refinements of hydraulic reaction valve performance relating to the operation of the valve in straight ahead driving.
- the steering gear operates substantially without any boost or assist, so that the self-aligning forces of the tyres are not opposed by the steering gear, so ensuring that the driving 'feel' is retained.
- the hydraulic reaction valve is held inoperative in this regime so optimizing on-centre 'feel'.
- the orifice areas defined by the slot edges of the valve core and sleeve must be large when the valve is in the centred position so that initial rotation of the valve elements changes the area proportionally only a small amount.
- the contour curve again, beyond the zone referred to where it approaches at 45° to the valve surface, to become concentric with the valve surface.
- the contour has the appearance of an arc of a circle, subtending an angle of say 45 0 , having its centre lying near the surface of the valve core adjacent the sleeve slot edge in the valve centred portion, but displaced into the underlapped zone. Beyond the point where the contour lies concentric to the valve core axis, it again curves towards the valve axis.
- this arrangement provides a 'hump' in the valve core edge contours which lie beneath the inner cylindrical surface of the sleeve and that the area defined by the gap between the sleeve and valve core does not change upon initial rotation of the valve elements from the centered position. This ensures that there will be no 'boost' or assist in the on-centre driving mode. Upon slight further rotation, however, the contour just described provides a rapid commencement of boost as in hydraulic reaction valves.
- the orifice can be made to act when in the on-centre driving.regimeas a venturi having a short zone of minimum cross-sectional area, bounded on each side by zones which gradually enlarge in sectional area, which arrangement produces far less pressure drop to fluid flow than a sharp-edged orifice having the same sectional area.
- This serves the purpose of reducing the back pressure of the valve and thus reducing the energy consumed by the power steering pump in this on-centre driving regime, the predominant mode of steering operation. Note that this reduced back pressure is accomplished without employing excessive underlap referred to earlier as used by some prior art devices.
- a valve core slot edge takes the form of a smoothly changing contour having three points of inflection, the first referred to earlier in connection with the high pressure region, and an additional two points of inflection occurring in the low pressure on-centre region.
- the latter two inflection points are such as to produce a venturi-like orifice with a zone of least sectional area on-centre adjoined on each side thereof by zones of gradually enlarging sectional area. After some slight valve rotation the orifice closes rapidly.
- a typical valve made according to the foregoing description may have six slots in the sleeve and six slots in the valve core, all twelve edges of the valve core slots having the contour just described. (In some cases more or less sets of slots in the valve components may be used, but never less than two sets). These twelve edges will be connected in pairs via the drilled passages in the sleeve and valve core referred to earlier, to the pump inlet and return ports and to the assist cylinders, the first edges of each pair controlling the inlet of oil to the cylinders and the second edges of each pair controlling the exhaust from the cylinders to the return port. Thus all three sets of edges are acting in parallel at all times.
- valve core slot edge contours which are the prime subject of this invention
- such differences of contour from edge to edge or along their length will generally detract from optimum performance.
- the loss of performance may be acceptable if the optimum contour described above is used along a large part of the length of some of the slot edges, but never less than 2 sets (4 edges), with a non-preferred form used over the remaining edges or portion of the edges.
- Reducing the length of the preferred edge contour and using a non-preferred form over other parts of the total length reduces the demands on accuracy compared with the high pressure, feather orifice.
- the part or parts having a non-preferred form may however, incorporate the venturi feature.
- the present invention consists in a core for a rotary valve for a power steering system in which at least two sets of valve core edges have, along a substantial portion of their length, a contour which extends substantially parallel to the core axis characterised in that the contour comprises in section a continuous curve wherein, at points near the high operating pressure zone thereof, it has a large radius of curvature and lies substantially parallel to the valve core periphery and wherein at a point along the curve approaching the coacting edge of an adjacent sleeve land edge when in the neutral position of the valve it lies at a steep slope to the valve core periphery with a curve of progressively smaller radius therebetween.
- the contour in the direction towards the low pressure operating zone reverses in curvature so.that the valve edge contour again approaches parallelism with the valve core periphery.
- said reversed curvature continues so that the valve contour again departs from parallelism so defining an orifice which, in the neutral position of the valve, has, for either direction of flow, a smoothly and continuously enlarging sectional area.
- valve housing 1 is provided with pump inlet and return connections 2 and 3 respectively and right and left hand cylinder connections 4 and 5.
- Steering gear housing 6, to which valve housing 1 is attached, contains the mechanical steering elements, for example, pinion 7, journalled by ball race 8 and provided with seal 9.
- the three main valve elements comprise valve core 10, sleeve member 11 journalled thereon, and torsion bar 12. This torsion bar is secured by a pin 12a to the valve core at one end similarly by pin 12b to pinion 7 at the other. It also provides a journal for valve core input shaft 10 by way of a bush as at 14.
- Sleeve member 11 has an annular extension having therein a slot 15 engaging pin 16 extending radially from pinion 7.
- valve core 10 and sleeve member 11 incorporate in their mating surfaces a plurality of longitudinally extending, blind-ended slots 18 and 19 respectively.
- Sleeve 11 is also provided on its outer periphery with a series of axially spaced circumferential grooves 17a, 17b, 17c separated by seals.
- Radial holes 20 (Fig. 2) in valve core 10 connect alternate slots 18 to the centre hole 10a in the valve core whence return oil can flow to pump return connection 3.
- valve sleeve 11 connects the remaining alternate slots 18 of the valve core to the centre circumferential groove 17b and so to inlet port 2.
- Other slots 19 are connected by radial holes 22 to corresponding circumferential grooves 17a and 17c and so to cylinder ports 4 and 5.
- Fig. 2 it will be seen that, in the neutral position of the valve illustrated, the twelve longitudinal slots 18 and 19 of the valve core and sleeve respectively are so shaped as to provide twelve elongated orifices 23 which vary in area as relative rotation of the sleeve and valve core occurs.
- valve operates to direct oil to and from the left and right cylinder ports 4 and 5
- valves operate to direct oil to and from the left and right cylinder ports 4 and 5
- the featuring of the edges of valve slot edges 18 to improve modulation of the valve is also a common practice.
- Fig. 3 shows in section to a greatly enlarged scale, the contour of one of the twelve orifices 23, (as for example, an inlet orifice to a left turn slot circles in Fig. 2), when the valve is in the centred condition.
- Oil entering the orifice area from slot 18 encounters a smoothly narrowing orifice or throat having least sectional area at point 26 where valve sleeve edge 25 is closest to the adjoining featured slot edge of the valve core. Beyond this point and up to corner 27 the orifice smoothly enlarges in sectional area as the valve core slot edge is in the form of a radius about point 28 displaced to the left of sleeve slot edge 25.
- This passage constitues a venturi orifice, whose restriction to the flow of oil is far less than that of an orifice having a sharp corner as for example, had the valve core slot edge had the form shown by dotted line 29.
- Such a form of edge is typical of the ground valve edge referred to earlier.
- the pressure drop through the valve in the neutral or centre-driving condition determines the energy consumed by the power steering pump in straight ahead high-speed driving, which of course, must be kept to a minimum value.
- valve core contour to the left of point 27 in Fig. 3, takes the form of an elongated scroll as shown in Fig. 4
- the sleeve slot edge 25 corresponds to its position in the on-centre condition illustrated in Fig. 3, and 25a its position when the distance 25-26 (Fig. 3) equals distance 25a-27.
- the orifice comprises, at least to the right of that point, a smoothly enlarging orifice which tends to prevent flow separation and hence hissing noises within the valve attributable to cavitation.
- Fig. 6 a non-preferred embodiment is shown in which the mode of operation of the valve just described applies only to that portion along the length of the valve contour between points 35 & 36 housing a section as shown in Fig. 6B. Thereafter, between points 36 & 37, the section is as shown in Fig. 6C.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Power Steering Mechanism (AREA)
Abstract
Description
- This invention relates to the cores of rotary valves of power steering gears, principally of the type wherein the valve core is also the input shaft to the steering gear.
- Typically such a valve core has, in its outer periphery, a plurality of blind ended, longitudinally extending slots separated by lands. Journalled on the valve core is a sleeve member having in its bore a similar array of longitudinally extending blind ended slots matching those of the valve core, but in underlap relationship thereto, the slots of the one being wider than the lands of the other so defining a set of longitudinally extending orifices which open and close when relative rotation occurs between the valve core and the sleeve.
- Drilled passages in the valve core and sleeve, together with circumferential grooves in the periphery of the sleeve, serve to communicate oil between the slots in the valve core and sleeve, an engine driven oil pump, and right-hand and left-hand hydraulic assist cylinder/chambers incorporated in the steering gear.
- All of-this is well known in the art of power steering gear design (for example as taught in U.S. Patent 3,022,722) including the use of a torsion bar incorporated in the valve core which serves to bias the valve and sleeve towards a neutral, centred condition when no power assistance is required. When torque is applied by the driver to the steering wheel, the torsion bar deflects, causing relative rotation of the sleeve and valve core from the neutral condition, so directing oil to the right-hand and left-hand assist cylinders.
- Such relative rotation of the valve elements will be directly proportional to the torque applied by the driver, so that if the edges of the slots are rectilinear, the area change of the aforesaid orifices will also be linear, and, as is well known in the art of such valves, the resulting pressure rise applied to the assist cylinders will be of an exponential form. The characteristic assist provided by such a valve will therefore be of a highly non-linear type. In constrast to this, the assist characteristic provided by the far more complex and formerly widely used hydraulic reaction power steering valve is truly linear over much of its operating range, as described in Automobiletechniche Zeitschrift 74(1972, page 62). A means of making the relatively simple torsion bar centred rotary valve simulate this aspect of the superior performance of the hydraulic reaction valve is described in U.S. patent 3,591,136.
- According to that patent the edges of the valve core slots are substantially radial to the valve axis, but contoured along their length so that, upon relative rotation of the valve elements, shut-off occurs progressively along the valve. This progressive phase of shut-off is such that the rate of area change is exponential, so that the rise in oil pressure is directly proportional to valve rotation as the driver applies torque to the steering wheel, so causing the valve to simulate this aspect of the action of the hydraulic reaction valve. As shut-off is approached, and the valve is operating at near-maximum pressure, a short pocket of limited radial depth remains open to the flow of oil but closes rapidly on further rotation of the valve elements as in hydraulic reaction valves. Further important aspects of the hydraulic reaction valve, relating to the performance of the valve in the neutral or on-centre driving region are imperfectly simulated in valves made according to that patent, as will be discussed later.
- Valves conforming to U.S. patent 3,591,136 have been widely applied to integral steering gears for several years, but are proving unsatisfactory for use in the more recently preferred rack and pinion type power steering gears, due to the fact that valve metering of the type described in that patent tends to produce hissing noises when operating at other than low pressures. Rack and pinion steering gears are now often mounted directly to the engine compartment bulk-head, and such noises are therefore far more apparent to the driver as they are transmitted directly to the car interior.
- It has been found that these noises can be greatly reduced if the design of the contour of the valve core slot edges is such that the oil flows in a thin 'sheet' or 'feather', which may be accomplished by having the edges of the valve core slots which operate at high pressures formed in such a manner that they are substantially of the same cross-section along their length, so producing a jet of oil, which is in the form of an elongated sheet a few micrometers thick. This is in contrast to the slot edge configuration shown in patent 3,591,136, which provides a short, thick jet of oil when the valve is operating at high pressures, only the short pocket referred to earlier remaining open. Examples of use of the 'sheet flow' hiss-suppressing technique are to be found in several Japanese manufactured steering gears, where the slot edges are each ground over their full length along the valve axis by causing a large cylindrical grinding wheel having its axis of rotation parallel to the valve core to grind one or more short flats on the slot edges almost tangential to the valve periphery.
- Now, according to the present invention, in order to provide valve slot edges having an exponential rate of area cut-off and other geometric features which will be referred to later needed to simulate the hydraulic reaction type valves various specific proportions of the valve edges are required.
- Firstly the cross-section of the slot edges of constant cross-secion which are able to provide the exponential rate of area change has a scroll-like contour extending about .6mm around the valve periphery, terminating, at the high pressure end thereof, in a surface nearly concentric with the valve axis.
- At the low-pressure end of the contour corresponding to the position of the valve elements as they approach the on- centre driving region, the slot edges become inclined at nearly 450 to the said surface. Secondly, in order to simulate the final rapid close-off characteristic of the hydraulic reaction valve, final close-off of the valve must occur rapidly, and hence the curvature of the contour at the high pressure end must reverse beyond that point where the rate of close-off has become substantially zero.
- Preferred forms of valve core edges made according to the invention provide further refinements of hydraulic reaction valve performance relating to the operation of the valve in straight ahead driving. In this regime it is desirable that the steering gear operates substantially without any boost or assist, so that the self-aligning forces of the tyres are not opposed by the steering gear, so ensuring that the driving 'feel' is retained. The hydraulic reaction valve is held inoperative in this regime so optimizing on-centre 'feel'. In order that the torsion-bar- centred rotary valve simulate this characteristic, the orifice areas defined by the slot edges of the valve core and sleeve must be large when the valve is in the centred position so that initial rotation of the valve elements changes the area proportionally only a small amount. However, this means that a large amount of torsion bar deflection will occur before the pressure rises in the assist cylinders, and the steering gear will be very compliant and lack response in straight-ahead driving. This is in contrast to the sharp responses of the hydraulic reaction valve, which changes from the inoperative to operative mode upon very slight rotation of the valve elements.
- In valve cores made according to preferred forms of the invention this defect of prior art valves is avoided by having the contour curve again, beyond the zone referred to where it approaches at 45° to the valve surface, to become concentric with the valve surface. Preferably, in this region just described, the contour has the appearance of an arc of a circle, subtending an angle of say 450, having its centre lying near the surface of the valve core adjacent the sleeve slot edge in the valve centred portion, but displaced into the underlapped zone. Beyond the point where the contour lies concentric to the valve core axis, it again curves towards the valve axis. It will be seen that this arrangement provides a 'hump' in the valve core edge contours which lie beneath the inner cylindrical surface of the sleeve and that the area defined by the gap between the sleeve and valve core does not change upon initial rotation of the valve elements from the centered position. This ensures that there will be no 'boost' or assist in the on-centre driving mode. Upon slight further rotation, however, the contour just described provides a rapid commencement of boost as in hydraulic reaction valves.
- Furthermore, by carefully proportioning the contour just described the orifice can be made to act when in the on-centre driving.regimeas a venturi having a short zone of minimum cross-sectional area, bounded on each side by zones which gradually enlarge in sectional area, which arrangement produces far less pressure drop to fluid flow than a sharp-edged orifice having the same sectional area. This serves the purpose of reducing the back pressure of the valve and thus reducing the energy consumed by the power steering pump in this on-centre driving regime, the predominant mode of steering operation. Note that this reduced back pressure is accomplished without employing excessive underlap referred to earlier as used by some prior art devices.
- Thus it will be seen that, in preferred forms of the invention, a valve core slot edge takes the form of a smoothly changing contour having three points of inflection, the first referred to earlier in connection with the high pressure region, and an additional two points of inflection occurring in the low pressure on-centre region. The latter two inflection points are such as to produce a venturi-like orifice with a zone of least sectional area on-centre adjoined on each side thereof by zones of gradually enlarging sectional area. After some slight valve rotation the orifice closes rapidly.
- A practical means of making this complex contour is set out in co-pending European Patent Application numbered 85 3070191 'Improved Means for Manufacturing Components of Rotary Valves'.
- A typical valve made according to the foregoing description may have six slots in the sleeve and six slots in the valve core, all twelve edges of the valve core slots having the contour just described. (In some cases more or less sets of slots in the valve components may be used, but never less than two sets). These twelve edges will be connected in pairs via the drilled passages in the sleeve and valve core referred to earlier, to the pump inlet and return ports and to the assist cylinders, the first edges of each pair controlling the inlet of oil to the cylinders and the second edges of each pair controlling the exhaust from the cylinders to the return port. Thus all three sets of edges are acting in parallel at all times.
- As is well known in the art, it is not necessary to contour all slot edges similarly, and valves are used where edges are of differing contour except as required for symmetrical operation of the steering gear.
- For the valve core slot edge contours, which are the prime subject of this invention, such differences of contour from edge to edge or along their length will generally detract from optimum performance. However, the loss of performance may be acceptable if the optimum contour described above is used along a large part of the length of some of the slot edges, but never less than 2 sets (4 edges), with a non-preferred form used over the remaining edges or portion of the edges. Reducing the length of the preferred edge contour and using a non-preferred form over other parts of the total length reduces the demands on accuracy compared with the high pressure, feather orifice. The part or parts having a non-preferred form, may however, incorporate the venturi feature.
- The present invention consists in a core for a rotary valve for a power steering system in which at least two sets of valve core edges have, along a substantial portion of their length, a contour which extends substantially parallel to the core axis characterised in that the contour comprises in section a continuous curve wherein, at points near the high operating pressure zone thereof, it has a large radius of curvature and lies substantially parallel to the valve core periphery and wherein at a point along the curve approaching the coacting edge of an adjacent sleeve land edge when in the neutral position of the valve it lies at a steep slope to the valve core periphery with a curve of progressively smaller radius therebetween.
- In a preferred form of the invention the contour, in the direction towards the low pressure operating zone reverses in curvature so.that the valve edge contour again approaches parallelism with the valve core periphery.
- In a further preferred form said reversed curvature continues so that the valve contour again departs from parallelism so defining an orifice which, in the neutral position of the valve, has, for either direction of flow, a smoothly and continuously enlarging sectional area.
- In order that the nature of the invention may be better understood a preferred form thereof is hereinafter described, by way of example, with reference to the accompanying drawings, in which:-
- Fig. 1 is a longitudinal part-cross-sectional view of a rotary valve for a power steering system;
- Fig. 2 is a cross-sectional view on line A-A of Fig. 1 of the valve core and surrounding sleeve;
- Fig. 3 is a cross-sectional view to an enlarged scale of portions of a valve core and sleeve incorporating the invention, constituting an orifice for the flow of oil;
- Fig. 4 is a similar view to an enlarged scale of a portion of the orifice;
- Fig. 5 is a curve showing the relationship between angular movement of the valve and the difference in oil pressure P between the left and right hand assist cylinders; and
- Fig. 6 is a view of one edge of a valve slot seen looking radially inwardly with the corresponding sleeve slot edge shown in chain lines.
- Figs. 6a and 6b shown sections of Fig. 6 on lines B-B and C-C.
- Referring to Fig. 1, valve housing 1 is provided with pump inlet and
return connections hand cylinder connections 4 and 5. Steering gear housing 6, to which valve housing 1 is attached, contains the mechanical steering elements, for example,pinion 7, journalled by ball race 8 and provided with seal 9. The three main valve elements comprisevalve core 10,sleeve member 11 journalled thereon, andtorsion bar 12. This torsion bar is secured by apin 12a to the valve core at one end similarly bypin 12b topinion 7 at the other. It also provides a journal for valvecore input shaft 10 by way of a bush as at 14.Sleeve member 11 has an annular extension having therein aslot 15 engagingpin 16 extending radially frompinion 7. - Referring now to Fig. 2,
valve core 10 andsleeve member 11 incorporate in their mating surfaces a plurality of longitudinally extending, blind-endedslots Sleeve 11 is also provided on its outer periphery with a series of axially spacedcircumferential grooves valve core 10 connectalternate slots 18 to thecentre hole 10a in the valve core whence return oil can flow to pumpreturn connection 3. - Radial holes 21 in
valve sleeve 11 connect the remainingalternate slots 18 of the valve core to the centrecircumferential groove 17b and so toinlet port 2.Other slots 19 are connected byradial holes 22 to correspondingcircumferential grooves cylinder ports 4 and 5. - In Fig. 2 it will be seen that, in the neutral position of the valve illustrated, the twelve
longitudinal slots elongated orifices 23 which vary in area as relative rotation of the sleeve and valve core occurs. - The manner in which the valve operates to direct oil to and from the left and
right cylinder ports 4 and 5 is well known in the art of such valves and the featuring of the edges of valve slot edges 18 to improve modulation of the valve is also a common practice. - Fig. 3 shows in section to a greatly enlarged scale, the contour of one of the twelve
orifices 23, (as for example, an inlet orifice to a left turn slot circles in Fig. 2), when the valve is in the centred condition. - Oil entering the orifice area from
slot 18 encounters a smoothly narrowing orifice or throat having least sectional area atpoint 26 wherevalve sleeve edge 25 is closest to the adjoining featured slot edge of the valve core. Beyond this point and up tocorner 27 the orifice smoothly enlarges in sectional area as the valve core slot edge is in the form of a radius aboutpoint 28 displaced to the left ofsleeve slot edge 25. - This passage constitues a venturi orifice, whose restriction to the flow of oil is far less than that of an orifice having a sharp corner as for example, had the valve core slot edge had the form shown by dotted
line 29. Such a form of edge is typical of the ground valve edge referred to earlier. - Because the orifice is in the form of a venturi, the restriction to the flow of oil in the position shown is far less than that of the dotted line configuration notwithstanding that the distance 27-25 is greater than the distance 25-26. This is because, for a valve of the type indicated by
line 29, flow separation occurs in 4 places - at both sides ofcorner 25 and at both sides ofcorner 27, whereas for the valve made according to the invention, separation occurs only to the left edge ofcorner 25 of the sleeve slot. - The pressure drop through the valve in the neutral or centre-driving condition determines the energy consumed by the power steering pump in straight ahead high-speed driving, which of course, must be kept to a minimum value.
- In, and adjacent to the on-centre driving condition of the valve elements distance 25-26 remains constant and there is no change in restriction in any of the twelve orifices, and hence no pressure rise in the assist cylinders. Hence, in this region of operation, a condition of zero hydraulic assist is provided.
- Upon sufficient counter-clockwise relative rotation of
sleeve 11,point 27 will lie at the same distance fromsleeve slot edge 25 as doespoint 26, and the venturi effect will cease. Additional rotation will cause a rapid reduction of orifice area, and thus a rapid rise in restriction to the flow of oil, and hence a rapid rise in pressure. Meantime the corresponding orifice on the opposite side of valve core slot 18 (not shown) provides a substantially unrestricted path to the flow of oil, now at an increased pressure, to the right-hand assist cylinder. Thus the design of orifice contour illustrated provides two important features of the hydraulic reaction valve, namely, zero on-centre hydraulic assist and, thereafter, a rapid turn-around to a substantial degree of assist. - The valve core contour to the left of
point 27 in Fig. 3, according to the preferred form of the invention, takes the form of an elongated scroll as shown in Fig. 4 - The
sleeve slot edge 25 corresponds to its position in the on-centre condition illustrated in Fig. 3, and 25a its position when the distance 25-26 (Fig. 3) equalsdistance 25a-27. - Successive increments of movement of the
sleeve groove edge 25a thereafter are shown as 25b-----25e, and it will be seen that the normal distance between these points decreases rapidly at first as for example at 25a, but finally slowly as at 25e where thecontour 30 approaches parallelism with the valve core periphery, that is, concentricity with its axis. - The normal distances which occur at 25a-----25c decrease in an exponential manner in order that the pressure rise in this high operating pressure zone of the orifice is proportional to the relative angular displacement of
sleeve 11 andvalve core 10. - By this means a fixed raio of assist is provided over and above some threshold value of relative rotation after
point 25a is reached. Thus, in Fig. 5, P is the difference of pressure in the right and left cylinders, and ∝ is the angular deflection of the torsion bar. Upto point 3la corresponding to sleeveslot edge position 25a there is substantially no rise in pressure P. Beyond this threshold value P rises proportionally to increase of ∝ abovepoint 31. In a typical valve core made according to the invention the rate at whichedge 25 is approaching valve core surface decreases from a value of 170 pm/deg. forpoint 25b to a value of 15 pm/deg. for 25e, where it is almost concentric with the valve core surface. - On further relative rotation of
sleeve 11 such as occurs when 25approaches 25f the normal distance between thesleeve edge 25 and thecurve 30 of the valve core groove again decreases rapidly, so that the pressure again rises rapidly as atline 33 of Fig. 5. - It will be seen that, even when operating nearly closed as at 25d, the orifice comprises, at least to the right of that point, a smoothly enlarging orifice which tends to prevent flow separation and hence hissing noises within the valve attributable to cavitation.
- In Fig. 6 a non-preferred embodiment is shown in which the mode of operation of the valve just described applies only to that portion along the length of the valve contour between
points 35 & 36 housing a section as shown in Fig. 6B. Thereafter, betweenpoints 36 & 37, the section is as shown in Fig. 6C.
Claims (5)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AUPG990885 | 1985-03-26 | ||
AU9908/85 | 1985-03-26 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0196172A2 true EP0196172A2 (en) | 1986-10-01 |
EP0196172A3 EP0196172A3 (en) | 1987-07-01 |
EP0196172B1 EP0196172B1 (en) | 1990-11-14 |
Family
ID=3771001
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP86301549A Expired - Lifetime EP0196172B1 (en) | 1985-03-26 | 1986-03-05 | Improved rotary valve |
Country Status (6)
Country | Link |
---|---|
US (1) | US5267588A (en) |
EP (1) | EP0196172B1 (en) |
JP (1) | JP2505742B2 (en) |
BR (1) | BR8601312A (en) |
DE (1) | DE3675562D1 (en) |
IN (1) | IN164346B (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0337723A1 (en) * | 1988-04-12 | 1989-10-18 | Koyo Seiko Co., Ltd. | Hydraulic pressure control valve |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2719861B2 (en) * | 1991-12-13 | 1998-02-25 | 自動車機器株式会社 | Fluid control valve device |
EP0620790A1 (en) * | 1992-01-16 | 1994-10-26 | A.E. BISHOP & ASSOCIATES PTY. LTD. | Rotary valve for hydraulic power steering with reduced noise and linear boost characteristic |
US5549504A (en) * | 1992-10-23 | 1996-08-27 | A. E. Bishop & Associates Pty Limited | Manufacture of rotary valves |
JPH0811736A (en) * | 1994-06-24 | 1996-01-16 | Jidosha Kiki Co Ltd | Rotor for hydraulic rotary valve |
JPH11504882A (en) | 1995-05-05 | 1999-05-11 | ビショップ ステアリング プロプライエタリー リミテッド | Power steering gear valve |
JP2001301633A (en) * | 2000-04-25 | 2001-10-31 | Showa Corp | Fluid pressure type power steering device for vehicle |
US6499507B1 (en) | 2000-09-12 | 2002-12-31 | Ford Global Technologies, Inc. | Rotary valve |
CN100360364C (en) * | 2002-05-03 | 2008-01-09 | Trw汽车美国有限责任公司 | Power steering control valve |
ITRE20120014A1 (en) * | 2012-02-28 | 2013-08-29 | Ognibene Power Spa | DISTRIBUTOR DEVICE FOR DRIVING |
CN102678969B (en) * | 2012-05-11 | 2013-12-18 | 烟台开发区龙源电力燃烧控制工程有限公司 | Distributed three-function valve |
US10604178B2 (en) | 2017-02-23 | 2020-03-31 | China Automotive Systems, Inc. | Control assembly for power steering |
CN114215814B (en) * | 2021-12-02 | 2023-12-05 | 珠海格力大金精密模具有限公司 | Die change switch and method for connecting die change switch with cylinder |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3591136A (en) * | 1969-02-26 | 1971-07-06 | Arthur E Bishop | Rotary valve with curved valve slot |
FR2357415A1 (en) * | 1976-07-09 | 1978-02-03 | Bishop Arthur | ROTARY VALVES IMPROVEMENTS |
GB2102361A (en) * | 1981-07-02 | 1983-02-02 | Danfoss As | Hydraulic steering control apparatus |
EP0095965A1 (en) * | 1982-05-26 | 1983-12-07 | Bendiberica S.A. | Rotary hydraulic distributor, and process for manufacturing chamfered closing edges for the rotary element of such a distributor |
US4460016A (en) * | 1980-05-30 | 1984-07-17 | Toyoda Koki Kabushiki Kaisha | Rotary servovalve |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES502483A0 (en) * | 1981-05-26 | 1982-04-01 | Bendiberica Sa | IMPROVEMENTS IN ROTARY HYDRAULIC DISTRIBUTORS |
JPS59118577A (en) * | 1982-12-27 | 1984-07-09 | Koyo Jidoki Kk | Spool for rotary control valve of power steering gear and method of manufacturing said spool |
JPS6047025B2 (en) * | 1982-12-28 | 1985-10-19 | 自動車機器株式会社 | How to chamfer a valve rotor for a hydraulic rotary valve |
JPS59223565A (en) * | 1983-06-03 | 1984-12-15 | Nissan Motor Co Ltd | Rotary valve |
-
1986
- 1986-03-05 US US07/836,433 patent/US5267588A/en not_active Expired - Fee Related
- 1986-03-05 DE DE8686301549T patent/DE3675562D1/en not_active Expired - Lifetime
- 1986-03-05 EP EP86301549A patent/EP0196172B1/en not_active Expired - Lifetime
- 1986-03-19 IN IN225/CAL/86A patent/IN164346B/en unknown
- 1986-03-24 BR BR8601312A patent/BR8601312A/en not_active IP Right Cessation
- 1986-03-26 JP JP61066085A patent/JP2505742B2/en not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3591136A (en) * | 1969-02-26 | 1971-07-06 | Arthur E Bishop | Rotary valve with curved valve slot |
FR2357415A1 (en) * | 1976-07-09 | 1978-02-03 | Bishop Arthur | ROTARY VALVES IMPROVEMENTS |
US4460016A (en) * | 1980-05-30 | 1984-07-17 | Toyoda Koki Kabushiki Kaisha | Rotary servovalve |
GB2102361A (en) * | 1981-07-02 | 1983-02-02 | Danfoss As | Hydraulic steering control apparatus |
EP0095965A1 (en) * | 1982-05-26 | 1983-12-07 | Bendiberica S.A. | Rotary hydraulic distributor, and process for manufacturing chamfered closing edges for the rotary element of such a distributor |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0337723A1 (en) * | 1988-04-12 | 1989-10-18 | Koyo Seiko Co., Ltd. | Hydraulic pressure control valve |
Also Published As
Publication number | Publication date |
---|---|
JPS61287862A (en) | 1986-12-18 |
DE3675562D1 (en) | 1990-12-20 |
EP0196172B1 (en) | 1990-11-14 |
JP2505742B2 (en) | 1996-06-12 |
EP0196172A3 (en) | 1987-07-01 |
US5267588A (en) | 1993-12-07 |
IN164346B (en) | 1989-02-25 |
BR8601312A (en) | 1986-12-02 |
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